Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D43/00—Automatic clutches
  • F16D43/02—Automatic clutches actuated entirely mechanically
  • F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
  • F16D43/06—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating axially a movable pressure ring or the like
  • F16D43/08—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating axially a movable pressure ring or the like the pressure ring actuating friction plates, cones or similar axially-movable friction surfaces
  • F16D43/09—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating axially a movable pressure ring or the like the pressure ring actuating friction plates, cones or similar axially-movable friction surfaces in which the carrier of the centrifugal masses can be stopped
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
  • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
  • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
  • F16H3/721—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously the secondary drive being an energy dissipating device, e.g. regulating brake, in order to vary speed continuously
  • F16H3/722—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously the secondary drive being an energy dissipating device, e.g. regulating brake, in order to vary speed continuously the secondary drive being a fluid throttle
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
  • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
  • F16H61/0293—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being purely mechanical
  • F16H61/0295—Automatic gear shift control, e.g. initiating shift by centrifugal forces

Definitions

• the method for controlling a transmission device is characterized in that the additional biasing means are activated. so that they apply by means of selective coupling a force which surpasses that of centrifugal weights tending to couple the coupling means only if the force of the weights corresponds to a speed making it possible to pass from the longer to the shorter of the two transmission reports without risk of overspeed at the input of the device.
• FIG. 1 is a schematic longitudinal sectional view of a four-speed transmission comprising several successive transmission devices according to the invention, at rest at the top of the figure and in neutral at the bottom of the figure;
• the four-speed transmission shown in FIG. 1, intended in particular for an automobile, * comprises three successive transmission devices -or modules 1a, 1b, 1c, with two ratios each, mounted in series between an input shaft 2a and an output shaft 2c of the transmission.
• the input shaft 2a also constitutes the input shaft in the module la. It is connected to the output shaft of a vehicle engine 5 without interposing the clutch.
• the output shaft 2c constitutes at the same time the output shaft of the module le and comprises a toothed wheel intended to drive by meshing the input of a differential for driving the driving wheels of a vehicle. Between the toothed wheel and the input of the differential can be interposed a forward / reverse reverse switch with manual control.
• the intermediate shaft 2ab is immobilized axially by axial support, with freedom of relative rotation, against the input shaft 2a by means of an axial stop Bl.
• the intermediate shaft 2bc and the output shaft 2c are each supported by a rolling bearing 3bc, 3c relative to the casing 4.
• Each module is capable of operating as a reducer or direct drive.
• a first report is produced when the three modules operate as a reduction gear, a second report when the first module operates it in direct drive and the other two as a reduction gear, a third report with the first two modules la and lb in direct drive and the third the in reducer, and a fourth report with the three modules in direct drive.
• the belleville spring 34 transmits to the cage 20, by means of the counterweights 29 in abutment at rest, a force which tightens the clutch 18b so that the input 2ab of the module lb is coupled in rotation with the output 2bc and the module constitutes a direct connection capable of transmitting torque up to a certain maximum defined by the clamping force of the belleville spring.
• the teeth of the crown 8, of the satellites 11 and of the planetary wheel 9 are of the helical type.
• the helical tilting direction of the teeth is chosen so that the direction of the axial thrust Pac originating in the crown 8 when it transmits a driving torque is such that the movable plate 27, driven axially by the crown 8, deviates of the clutch retaining plate 26.
• the planet carrier 13a can rotate in reverse by driving the hub 111 with it by the free wheel 16a, which causes pumping in the direction shown in FIG. 6.
• the valve 40 is opened to automatically achieve a neutral position, ie uncoupling between the input shafts 2a and output 2c when the vehicle is stationary (output shaft 2c stationary) while the input shaft 2a turned. It is thanks to this function that the clutch or the torque converter traditionally mounted between the engine 5 and the transmission can be eliminated.
• the valve 40 is gradually closed to progressively brake the rotor 37 by means of an increasing pressure drop through the valve 40.
• modules all essentially identical, spontaneously organize to achieve a gradual shift of gear ratios.
• the differences that have been described with respect to module la have no bearing on this.
• the one which downshifts is always the one which is the closest functionally to the output shaft 2c, it can be provided that the modules have all the fewer weights, or weights that are all the lighter, or even less disks in their clutch, that they are functionally closer to the outlet. But it is simply a question of nuancing the response to the transmitted torque, with variations of a few% from one module to the neighbor.
• the rotor 37 adds its inertial effect to that of the traditional flywheel of the heat engine 5.
• This is very advantageous because the flywheel of a heat engine is especially useful during idling for avoid that the engine, not connected to an inertial load, is unable to continue its rotation when a piston of the heat engine arrives at the end of gas compression.
• the steering wheel inertia of the traditional heat engine strikes the acceleration performance of the vehicle.
• the rotor 37 rotating only when the vehicle is stopped, on the one hand the same idling stabilization is obtained with a smaller flywheel on the motor 5, and in addition the inertia of the rotor 37 disappears during normal operation since the rotor 37 is then stopped.

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Structure Of Transmissions (AREA)
• Control Of Transmission Device (AREA)
• Arrangement Of Transmissions (AREA)
• Gear-Shifting Mechanisms (AREA)
• Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
• Transmission Devices (AREA)
• Cash Registers Or Receiving Machines (AREA)
• Control Of Driving Devices And Active Controlling Of Vehicle (AREA)
• Retarders (AREA)
• One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
• Automobile Manufacture Line, Endless Track Vehicle, Trailer (AREA)

Applications Claiming Priority (3)

Publications (2)

Family

ID=9444180

Family Applications (1)

Country Status (21)

Cited By (2)

Families Citing this family (10)

Family Cites Families (5)

• 1993
  • 1993-02-18 FR FR9301841A patent/FR2701747B1/fr not_active Expired - Fee Related
• 1994
  • 1994-02-17 AU AU61104/94A patent/AU695026B2/en not_active Ceased
  • 1994-02-17 DK DK94907587.3T patent/DK0683877T3/da active
  • 1994-02-17 DE DE69403196T patent/DE69403196T2/de not_active Expired - Fee Related
  • 1994-02-17 BR BR9406124A patent/BR9406124A/pt not_active IP Right Cessation
  • 1994-02-17 CZ CZ19952046A patent/CZ292450B6/cs not_active IP Right Cessation
  • 1994-02-17 CA CA002156163A patent/CA2156163A1/fr not_active Abandoned
  • 1994-02-17 UA UA95094155A patent/UA44239C2/uk unknown
  • 1994-02-17 ES ES94907587T patent/ES2104353T3/es not_active Expired - Lifetime
  • 1994-02-17 AT AT94907587T patent/ATE153113T1/de not_active IP Right Cessation
  • 1994-02-17 EP EP94907587A patent/EP0683877B1/de not_active Expired - Lifetime
  • 1994-02-17 HU HU9502412A patent/HU220500B1/hu not_active IP Right Cessation
  • 1994-02-17 CN CN94191226A patent/CN1056681C/zh not_active Expired - Fee Related
  • 1994-02-17 RO RO95-01482A patent/RO114996B1/ro unknown
  • 1994-02-17 RU RU95121697A patent/RU2117199C1/ru not_active IP Right Cessation
  • 1994-02-17 JP JP51870394A patent/JP3585923B2/ja not_active Expired - Fee Related
  • 1994-02-17 SK SK1016-95A patent/SK279569B6/sk unknown
  • 1994-02-17 KR KR1019950703448A patent/KR100289360B1/ko not_active Expired - Fee Related
  • 1994-02-17 WO PCT/FR1994/000176 patent/WO1994019629A1/fr not_active Ceased
  • 1994-02-18 ZA ZA941142A patent/ZA941142B/xx unknown
• 1997
  • 1997-07-23 GR GR970401870T patent/GR3024224T3/el unknown

Non-Patent Citations (1)

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